EP2853822A1 - Système de contrôle de pompe - Google Patents

Système de contrôle de pompe Download PDF

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Publication number
EP2853822A1
EP2853822A1 EP13186152.8A EP13186152A EP2853822A1 EP 2853822 A1 EP2853822 A1 EP 2853822A1 EP 13186152 A EP13186152 A EP 13186152A EP 2853822 A1 EP2853822 A1 EP 2853822A1
Authority
EP
European Patent Office
Prior art keywords
pump
pressure
flow rate
rotational speed
change
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP13186152.8A
Other languages
German (de)
English (en)
Inventor
Jussi Tamminen
Tero Ahonen
Jero Ahola
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ABB Schweiz AG
Original Assignee
ABB Oy
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ABB Oy filed Critical ABB Oy
Priority to EP13186152.8A priority Critical patent/EP2853822A1/fr
Priority to US14/489,203 priority patent/US20150086382A1/en
Priority to CN201410498531.8A priority patent/CN104514705B/zh
Publication of EP2853822A1 publication Critical patent/EP2853822A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D7/00—Control of flow
    • G05D7/06—Control of flow characterised by the use of electric means
    • G05D7/0617—Control of flow characterised by the use of electric means specially adapted for fluid materials
    • G05D7/0629—Control of flow characterised by the use of electric means specially adapted for fluid materials characterised by the type of regulator means
    • G05D7/0688—Control of flow characterised by the use of electric means specially adapted for fluid materials characterised by the type of regulator means by combined action on throttling means and flow sources
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1009—Arrangement or mounting of control or safety devices for water heating systems for central heating
    • F24D19/1012—Arrangement or mounting of control or safety devices for water heating systems for central heating by regulating the speed of a pump
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the invention relates to pumping system control, and particularly to a control method and arrangement according to the preamble of the independent claims.
  • a pumping system has the best preconditions for operating energy efficiently when the losses are minimized. This may be obtained, for instance, by minimizing the flow resistance in a piping system by opening the control valves to their maximum and using the smallest pressure that satisfies the system requirements or selecting the rotational speed that results in the lowest specific energy consumption.
  • each branch comprises a control valve to control the amount of fluid flowing through the branch
  • each branch comprises a control valve to control the amount of fluid flowing through the branch
  • these systems work most energy efficiently when a control valve is opened completely, the pump pressure is controlled according to the flow rate through this valve, and the other valves control the flow rate through their respective branch according to the requirement of flow rate with throttling.
  • this method requires valve setting or angle information to be retrievable from a control system or from a direct feedback from the valve. This requires additional instrumentation and wiring, increasing the system costs and providing a further source of failure, and in many cases, as in connection with a thermostat-controlled radiator based heating system for example, this information is not available in the first place.
  • An object of the present invention is thus to provide a new method and a new arrangement for controlling pump systems.
  • the objects of the invention are achieved by a method and an arrangement characterized by what is stated in the independent claims. Preferred embodiments of the invention are disclosed in the dependent claims.
  • the invention is based on the idea of utilising known and/or determined pump characteristics and easily determined pressure and/or rotational speed of the pump and flow rate information to find and control a pump pressure setting that optimises the energy efficiency of the system.
  • An advantage of the method and arrangement of the invention is that the efficiency of pumping systems comprising two or more branches, each comprising an independently adjustable control element, can be significantly improved with no need for information about valve settings or angles. Thus, additional instrumentation and wiring can be avoided.
  • FIG. 1 schematically illustrates a pump system.
  • the pump system comprises a pump 2 and at least two branches 3.
  • the pump system 1 comprises three branches 3.
  • Each of the branches may comprise a flow control element 5, and pump control means (not shown), such as a variable speed drive, a variable frequency drive, an inlet vane guide and/or a control element, may be provided in connection with the pump 2.
  • the pump system 1 comprises a heating system, wherein each of the branches 3 comprises a load element 4, more particularly a heating element, and a flow control element 5, more particularly a thermostat.
  • the pump system also comprises a thermal transfer element 6.
  • This embodiment is shown as an example only and it is clear to a person skilled in the art that the configuration of the pump system may vary in different embodiments within in the scope of the claims.
  • FIG. 2 schematically illustrates a method of controlling a pump.
  • a total flow rate through the pump is measured 201 before a pump pressure change
  • the pump pressure is changed 202 by a predetermined pressure step
  • a total flow rate through the pump is measured 203 after the pump pressure change
  • a need for a further pump pressure change step is determined 204 on the basis of the total flow rate measurement carried out before and after the pump pressure change.
  • a new pressure change step is only to be started once a sufficient time has elapsed since the previous pressure change step to enable the pump system to reach a steady state again.
  • This time interval for starting a new pressure change step is now called an execution time interval and it should be defined separately for each system and embodiment since because it depends on the embodiment and system size, it may range from seconds to several minutes or even to several hours in some embodiments, for example.
  • a settling time in other words the time for the pump system to reach a steady state, may be determined with a step response test.
  • a pressure that is known to be sufficient to satisfy the system demand is preferably used at the start.
  • the pressure may be increased in a step-wise manner.
  • an estimate of the settling time can be calculated from the time domain change of the total flow rate.
  • a pressure step may be introduced in to the system, causing a step-wise increase in the rotational speed and flow rate of the pump.
  • the settling time of the constant pressure control in connection with the individual branch flow rate control elements is found and may be used as an execution time interval in the control method of the present solution as such or as a basis for the determination of the execution time interval.
  • the settling time is determined as the time from the start of the step, in other words the pressure or rotational speed change, to the moment of time when the flow rate (estimate) has reached a value within 2 per cent of its final value. It should be noted that the settling time may vary according to the system operating point, meaning for example that the settling time at lower total flow rates may differ from the settling time at higher total flow rates.
  • FIG 3 schematically illustrates an embodiment of a method of controlling a pump system as a flow chart.
  • This embodiment implements a control algorithm according to an embodiment of the present solution.
  • the pump may be controlled to a steady state by controlling the pump pressure, which is called a pressure reference H ref in Figure 3 .
  • the total flow rate Q may be measured and compared with a flow rate change threshold value.
  • a pressure change may be introduced in response to the total flow rate exceeding the threshold value or a dead time threshold being reached.
  • DT refers to dead time loop index
  • DT TH refers to a dead time threshold in loops to check the sufficiency of the pump pressure
  • H step refers to a pressure change step
  • H ref refers to a pressure reference
  • Q refers to a total flow rate
  • Q prev refers to a total flow rate of the previous loop
  • TH refers to a threshold for the flow rate as a relative value from 0 to 1.
  • a need for a pressure change may be determined in response to detection of a reduced flow rate.
  • the current flow rate may then be saved as Q prev and the pressure reference may be lowered by a predetermined pressure change step of the amount of H step .
  • the current pump flow rate Q which can be measured when the system has again reached a steady state after the pressure change, may then be compared with the previous flow rate Q prev according to the threshold criterion TH. In other words, it is checked whether the pressure change has caused a change in the total flow rate that exceeds the relative threshold value.
  • the pump pressure may be changed by a predetermined pressure step until a substantial change between a current pump flow rate Q and the previous total flow rate Q prev is detected.
  • the change is considered substantial when the relative threshold has been exceeded.
  • the pump may be returned to the previous pump pressure value that is the pressure before the latest pressure changing step.
  • an optimal pump pressure for the pump system in current operating conditions has been found and set and no further pressure change is needed until otherwise indicated.
  • this branch or state is called Reduce pressure.
  • a need for a pressure change may be determined in response to detection of an increase in the total flow rate above the threshold value.
  • the algorithm proceeds to the state called Increase pressure.
  • the pressure is increased step-wise until the total flow rate does not increase.
  • the previous pressure is the lowest pressure that satisfies the demand and it is used as the pressure reference.
  • this branch or state is called Increase pressure.
  • the pump system may be configured to initiate a change in the pump pressure at predetermined time intervals equal to dead time threshold DT TH .
  • a need for a pressure change may be determined in response to a time interval equal to dead time threshold having elapsed since a previous pump pressure change, when no recognizable change has been detected total flow rate during the time interval.
  • this pressure change comprises increasing the pressure. This enables a sufficient pressure to be provided in a branch in which a valve has been fully opened because of an earlier pressure reduction, since at that point it cannot be known whether that particular branch requires more flow. A sufficient pressure in each of the branches can be ensured by testing regularly that the pressure remains at the required level in a manner similar to that disclosed above in connection with other embodiments.
  • the dead time threshold should be greater than the execution time interval. According to an embodiment, the dead time threshold is equal to a multiple of the execution time interval.
  • a sensorless implementation can be based on model-based pump operating point estimation methods known per se. These estimation methods may comprise using pump characteristic curves, such as the examples illustrated in Figures 4a and 4b , affinity laws known per se as a model of the pump, and frequency converter estimates of the motor rotational speed and shaft power as inputs.
  • the characteristics and general performance of a centrifugal pump for example, can be visualized by characteristic curves for the pressure or head H, shaft power consumption P and efficiency ⁇ as a function of the flow rate Q at a constant rotational speed.
  • the best efficiency point (BEP) of a centrifugal pump, in which the pump should be typically driven, is typically also provided by the pump manufacturer.
  • a frequency-converter-driven pump for example, can be operated at various rotational speeds and, thus, the pump characteristic curves need to be converted into the current rotational speed. This can be performed on the basis of flow rate, pump pressure, pump shaft power consumption and rotational speed utilizing affinity laws known per se.
  • the pump characteristic curves enable the sensorless estimation of the pump operating point location and efficiency by utilizing the rotational speed and shaft torque estimates ( n est and T est , respectively) available from a frequency converter in a manner known per se.
  • FIG. 5 schematically illustrates a block set diagram of the pump system control according to an embodiment of the present solution.
  • a control algorithm is executed at an execution time interval T.
  • the execution time interval is preferably equal to or longer than the time needed for the pump system to reach a steady state after a previous pressure change.
  • the execution time interval is preferably equal to or longer than the settling time.
  • the pump is constant pressure controlled during the operation.
  • the constant pressure control may be executed constantly to ensure a constant pressure of the pump such that an effect of an individual branch flow control element does not affect the pump pressure.
  • this constant pressure control can be achieved by a sensorless model-based operating point estimation method as presented in Figure 5 .
  • an error between a desired and the estimated pressure may be calculated and inputted to a PID controller.
  • the PID controller may calculate a new rotational speed reference for the pumping system.
  • the frequency converter may then adjust the rotational speed and estimate the power, which may then be used to estimate the produced pressure and flow rate.
  • the flow rate estimate can be used in the algorithm and the pressure estimate for control purposes in the constant pressure control as explained above.
  • the size of the predetermined pressure step or the step-wise change of the pressure reference H step is related to the flow rate threshold TH.
  • the flow rate threshold may be used to determine whether the total flow rate in the system has remained unchanged regardless of the change in the pressure.
  • the pressure change step should preferably be selected to be such that it is able to produce a notable change in the system total flow rate.
  • FIG. 6 schematically illustrates an arrangement for pump system control.
  • the pump system may comprise a pump 2 and at least two branches 3 (three branches in the embodiment of Figure 6 ), wherein each of the branches comprises a flow control element 5.
  • a flow control element may comprise a flow control valve, for example.
  • the flow control element comprises a thermostat.
  • a control arrangement for a pump system may comprise pump control means 7 and means for measuring a total flow rate through a pump 8.
  • the pump control means may comprise a frequency converter and/or a control unit, for example. Such frequency converters and control units are known per se. In different embodiments, these means may be arranged separately or some or all of the means may be integrated in the pump.
  • the means for measuring the total flow rate may comprise at least one sensor and/or control element, for example. Such sensors and control elements are known as such and in some embodiments a common control element may be used for both the pressure control and flow rate measurement.
  • the pump control means may be configured to change the pump pressure by a predetermined pressure step and the means for measuring the total flow rate may be configured to measure the total flow rate before the pump pressure change and after the pump pressure change.
  • the pump control means may then further be configured to determine a need for a further pump pressure change step on the basis of said total flow rate measurements before and after the pump pressure change.
  • the pump 2 may comprise a pump, a fan or a compressor.
  • the pump system and/or the control arrangement may be used to implement one or more of the methods disclosed in this description or a combination thereof.
  • the pump system may comprise a three-branch pump system, wherein each of the branches comprises an independent flow control element, such as a flow controlling valve, such as the embodiment of Figure 1 .
  • the graphs start with the setup, in which the control valves are partially closed, the pump system is in balance and the execution time interval T is set at 50 seconds.
  • a step-wise change in the flow rate requirement for a single branch occurs starting at the time instant of 600 s as a result of a change in the system requirements.
  • the dead time threshold DT TH has been set to be 150 s.
  • the system starts to change the pump pressure step-wise by a pressure change step. Between time instants of 0 to 200 seconds, the pressure reduces step by step. Between time instants of 0 to 150 seconds, the total flow rate remains approximately the same, as the system has reached a steady state. However, at time instants of 150 to 200 seconds, the total flow rate is notably reduced because of an insufficient pressure. Therefore, at 200 seconds the pressure is increased back to a sufficient level. This means that the lowest pressure for the system is found.
  • the algorithm checks whether a pressure increase is required, but since the total flow rate stays approximately the same despite the pressure increase, the pressure is not increased permanently. However, at 750 seconds the flow rate increases significantly when the pressure is increased, meaning that a higher pressure reference is required to satisfy the demand. The pressure is increased until the increase in the pressure does not increase the flow rate significantly. Again, the lowest pressure satisfying the demand is found.
  • the system withstands some transients in the pressure and hence in the flow rate. Also, the system preferably withstands a certain amount of inaccuracy in the flow rate. Preferably, the settling time of the individual flow rate controls and pressure control should be faster than the change in the flow rate reference, whereby the flow rate demand would stay approximately constant during the pressure stepping.
  • FIG. 8 schematically illustrates a further method of controlling a pump.
  • a total flow rate through the pump is measured 801 before a pump rotational speed change
  • the pump rotational speed is changed 802 by a predetermined rotational speed step
  • a total flow rate through the pump is measured 803 after the pump rotational speed change
  • a need for a further pump rotational speed change step is determined 804 on the basis of the total flow rate measurement carried out before and after the pump rotational speed change.
  • This embodiment may be similar to any one or any combination of the embodiments explained in connection with the control based on a pump pressure change in other respects, but instead of pressure change steps, the rotational speed change steps are used.
  • any control arrangement explained in connection with the embodiments comprising a pressure change step may be used in connection with a rotational speed change step as long as the pump control means may be configured to change the rotational speed of the pump.
  • a new rotational speed change step is only to be started once a sufficient time has elapsed since the previous rotational speed change step to enable the pump system to reach a steady state again.
  • This time may also be called an execution time interval and it should be defined separately for each system and embodiment since because it depends on the embodiment and system size, it may range from seconds to several minutes or even to several hours in some embodiments, for example.
  • the pump system may comprise a pump, a fan or a compressor system or a combination thereof, wherein individual branch flow control elements are provided as long as allowed by the device and system characteristics.
  • the pump may comprise a pump, a fan or a compressor.
  • the current solution may be used in combination with the known solution of throttle control, when the system comprises information on the valve setting of critical branches in the system.
  • a combination of the both control methods provides an even more precise flow control, which may be particularly beneficial in some applications.
  • the methods may be combined, which leads to a situation where any system having flow rate control in a branch, whether it be known or unknown, can be optimized.
  • additional sensors such as pressure or flow rate sensors, may be provided for further improving the estimation accuracy of the model-based solutions in particular, thus also improving the operation of the present solutions.
  • the required pressure of a pumping system and, thus, the dynamic flow losses of the system that has individual flow control elements in each branch can be reduced.
  • the reduction in the flow resistances and the lower pressure lead to a better energy efficiency.
  • the implementation of the solution can be mainly carried out based on the model of the pump with very little additional information needed. No information about the individual control elements is required, contrary to known solutions.
  • the solution can be used along with the known solutions to ensure a pressure optimum in even more critical applications.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
EP13186152.8A 2013-09-26 2013-09-26 Système de contrôle de pompe Withdrawn EP2853822A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP13186152.8A EP2853822A1 (fr) 2013-09-26 2013-09-26 Système de contrôle de pompe
US14/489,203 US20150086382A1 (en) 2013-09-26 2014-09-17 Pumping system control
CN201410498531.8A CN104514705B (zh) 2013-09-26 2014-09-25 泵系统的控制

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13186152.8A EP2853822A1 (fr) 2013-09-26 2013-09-26 Système de contrôle de pompe

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EP2853822A1 true EP2853822A1 (fr) 2015-04-01

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EP13186152.8A Withdrawn EP2853822A1 (fr) 2013-09-26 2013-09-26 Système de contrôle de pompe

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US (1) US20150086382A1 (fr)
EP (1) EP2853822A1 (fr)
CN (1) CN104514705B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3168477A1 (fr) * 2015-11-10 2017-05-17 ABB Technology Oy Procédé et appareil d'estimation d'état de fonctionnement d'un compresseur à déplacement positif

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6037317B2 (ja) * 2012-08-09 2016-12-07 パナソニックＩｐマネジメント株式会社 モータ制御装置、モータ制御方法および送風装置
RU2724390C2 (ru) 2015-06-04 2020-06-23 Флюид Хэндлинг ЭлЭлСи Прямой численный аффинный бессенсорный преобразователь для насосов
EP3118458B1 (fr) * 2015-07-15 2017-08-30 ABB Technology Oy Procédé et appareil en relation avec un compresseur à vis
IT201700043015A1 (it) * 2017-04-19 2018-10-19 Abac Aria Compressa Compressore provvisto di pressostato elettronico e procedimento per regolare la pressione in un tale compressore.
CN108169394B (zh) * 2017-12-26 2019-11-29 迈克医疗电子有限公司 流量控制方法和装置、分析仪器及计算机可读存储介质

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Publication number Priority date Publication date Assignee Title
FR1427641A (fr) * 1963-04-23 1966-02-11 Vogel Pumpen Procédé et installation pour la régulation de pompes rotatives destinées à l'alimentation d'un réseau de consommation ou de circulation
DE19912588A1 (de) * 1999-03-20 2000-09-21 Ksb Ag Fluidtransportsystem
EP1323986A1 (fr) * 2001-12-24 2003-07-02 Grundfos A/S Méthode de commande pour une pompe à vitesse réglable d'une installation de chauffage
DE102007058211A1 (de) * 2007-12-04 2009-06-10 Siemens Ag Verfahren zum Betrieb eines strömungstechnischen Leitungssystems
DE102011012211A1 (de) * 2011-02-23 2012-08-23 Wilo Se Leistungsoptimiertes Betreiben einer elektromotorisch angetriebenen Pumpe durch Mitkopplung

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JPS5477301A (en) * 1977-12-01 1979-06-20 Toyo Electric Mfg Co Ltd Automatic on-off device of variable speed pump
US4836095A (en) * 1986-12-01 1989-06-06 Carrier Corporation Static pressure control in variable air volume delivery system
US4850805A (en) * 1987-03-13 1989-07-25 Critikon, Inc. Pump control system
US5863246A (en) * 1997-12-15 1999-01-26 Carrier Corporation Variable air volume control system
US6719625B2 (en) * 2001-09-26 2004-04-13 Clifford Conrad Federspiel Method and apparatus for controlling variable air volume supply fans in heating, ventilating, and air-conditioning systems
MY167120A (en) * 2006-11-10 2018-08-10 Oyl Res & Development Centre Sdn Bhd An apparatus for controlling an air distribution system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1427641A (fr) * 1963-04-23 1966-02-11 Vogel Pumpen Procédé et installation pour la régulation de pompes rotatives destinées à l'alimentation d'un réseau de consommation ou de circulation
DE19912588A1 (de) * 1999-03-20 2000-09-21 Ksb Ag Fluidtransportsystem
EP1323986A1 (fr) * 2001-12-24 2003-07-02 Grundfos A/S Méthode de commande pour une pompe à vitesse réglable d'une installation de chauffage
DE102007058211A1 (de) * 2007-12-04 2009-06-10 Siemens Ag Verfahren zum Betrieb eines strömungstechnischen Leitungssystems
DE102011012211A1 (de) * 2011-02-23 2012-08-23 Wilo Se Leistungsoptimiertes Betreiben einer elektromotorisch angetriebenen Pumpe durch Mitkopplung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3168477A1 (fr) * 2015-11-10 2017-05-17 ABB Technology Oy Procédé et appareil d'estimation d'état de fonctionnement d'un compresseur à déplacement positif

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US20150086382A1 (en) 2015-03-26
CN104514705B (zh) 2018-02-02
CN104514705A (zh) 2015-04-15

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